[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

EP0197339B1 - High tension circuit breaker with closing resistor - Google Patents

High tension circuit breaker with closing resistor Download PDF

Info

Publication number
EP0197339B1
EP0197339B1 EP86103192A EP86103192A EP0197339B1 EP 0197339 B1 EP0197339 B1 EP 0197339B1 EP 86103192 A EP86103192 A EP 86103192A EP 86103192 A EP86103192 A EP 86103192A EP 0197339 B1 EP0197339 B1 EP 0197339B1
Authority
EP
European Patent Office
Prior art keywords
lever
voltage switch
spring
switch point
switch according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP86103192A
Other languages
German (de)
French (fr)
Other versions
EP0197339A1 (en
Inventor
Walter Bischofberger
Heinz Eichholzer
Werner Graber
Edgar Hochspach
Werner Lüthi
Jiri Talir
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
BBC Brown Boveri AG Switzerland
Original Assignee
BBC Brown Boveri AG Switzerland
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by BBC Brown Boveri AG Switzerland filed Critical BBC Brown Boveri AG Switzerland
Publication of EP0197339A1 publication Critical patent/EP0197339A1/en
Application granted granted Critical
Publication of EP0197339B1 publication Critical patent/EP0197339B1/en
Expired legal-status Critical Current

Links

Images

Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/42—Driving mechanisms
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H33/00—High-tension or heavy-current switches with arc-extinguishing or arc-preventing means
    • H01H33/02—Details
    • H01H33/04—Means for extinguishing or preventing arc between current-carrying parts
    • H01H33/16—Impedances connected with contacts
    • H01H33/166—Impedances connected with contacts the impedance being inserted only while closing the switch
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H3/00—Mechanisms for operating contacts
    • H01H3/32—Driving mechanisms, i.e. for transmitting driving force to the contacts
    • H01H3/46—Driving mechanisms, i.e. for transmitting driving force to the contacts using rod or lever linkage, e.g. toggle

Definitions

  • the present invention relates to a high-voltage switch with on-resistance according to the preamble of claim 1.
  • a high-voltage switch is already known from the published patent application DE-A-3 132 821, in which the series connection of a secondary connection point with an on-resistance is connected in parallel with a main switching point.
  • the main switching point is actuated via a lever gear assigned to it, while another lever gear acts on a movable contact of the secondary switching point.
  • the lever gear assigned to the secondary switching point is designed such that the secondary switching point always closes before the main switching point when it is switched on and then opens again after the main switching point has been closed.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, solves the task of achieving a movement sequence in a generic high-voltage switch, which can be adapted to different network conditions in a simple manner while saving on components of the drive.
  • a drive 1 moves via an insulating drive rod 3 which is guided through an insulator column 2 and a shaft 5 via a lever arrangement 4.
  • the shaft 5 is mounted in a conductive deflection housing 6, which is only indicated and which is supported on the insulator column 2.
  • a rotary lever 7 which is non-positively fastened to the shaft 5 acts on a movable contact 9 of a main switching point 10 via a first thrust crank drive 8.
  • the movable contact 9 cooperates with a fixed contact 11 which is connected to a power connection 12.
  • a lever 15, which is non-positively fastened to the shaft 5, moves a movable contact 17 of a secondary switching point 18 via a second thrust crank drive 16.
  • the secondary switching point 18 is electrically connected in series with an on-resistance 19, and this series connection is parallel to the main switching point 10.
  • a flexible, conductive connection 20 between the power connection 12 and a fixed contact 21 of the secondary switching point 18 represents a parallel connection, while the other parallel connection is formed by the deflection housing 6.
  • the main switching point 10 and the series connection of secondary switching point 18 and switch-on resistor 19 are surrounded by insulating housings, not shown.
  • FIG. 2 shows the drive area of the secondary switching point 18 when the high-voltage switch is definitely switched off.
  • the lever 15 forms a push-through joint 23 with a hinged lever 22.
  • the end of the lever 22 facing away from the lever 15 comprises a joint bolt 24 and is connected to a first holder 25 of a spring element 26.
  • a second holder 27 of the spring element 26 is connected to a pivot point 28 arranged on the lever 15 adjacent to the shaft 5.
  • one end of a connecting rod 29 is articulated on the hinge pin 24, the other end of which is articulated to a guide piece 30.
  • This guide piece 30 slides in a cylindrical sleeve 32 connected to the deflection housing 6 via ribs 31 and is rigidly connected to the one end of an actuating rod 33 made of rod-shaped or tubular insulating material.
  • the other end of the actuating rod 33 penetrates the pierced disks of the on-resistance 19 and is with connected to the movable contact 17 of the secondary switching point 18.
  • a first impact ring 34 is seated on the actuating rod 33 and is additionally supported on the guide piece 30.
  • a second impact ring 35 is also rigidly attached to the operating rod 33.
  • two stops 36, 37 concentrically surround the actuating rod 33.
  • the two stops 36, 37 are supported on opposite sides on a common spring assembly 38 which can cushion them in the axial direction and become together with this carried by a bracket 39.
  • the bracket 39 is rigidly attached in the sleeve 32.
  • FIG. 6 shows a section through the spring element 26.
  • Each of the two brackets 25, 27 has an eyelet 45 for attachment and receives one end of a tension spring 46 which acts on the two brackets 25, 27 in the axial direction.
  • the bracket 25 partially includes the bracket 27 and guides the tension spring 46.
  • the bracket 27 carries a damping device 47 which is fastened by means of a retaining screw 48.
  • the retaining screw 48 holds a damper disk 49 so that it can slide in the axial direction along the shaft 48a thereof.
  • the damper disk 49 is acted upon on the one hand by a shoulder 50 of the holder 25 with the spring force of the tension spring 46 and on the other hand it is supported on a spring assembly 51 and presses it against a shoulder 52 of the holder 27.
  • a cylindrical friction spring assembly is shown schematically, such as e.g. in the arrangements according to FIG. 2 (spring assembly 38) and FIG. 6 (spring assembly 51) between force-transmitting parts, such as the two stops 36, 37, can be installed.
  • the friction spring assembly consists of outer spring rings 60 and inner spring rings 64, which are alternately stacked on top of one another.
  • Each outer spring ring 60 has conical bevels 61, 62 on the inside, which are designed identically from both sides and which meet in an edge 63.
  • Each inner spring ring 64 has conical chamfers 65, 66 on the outside, which are of identical design from both sides and which meet in an edge 67.
  • the chamfers 61 and 65 as well as 62 and 66 match each other exactly when the friction spring assembly is stacked.
  • End rings 68 which correspond to halved inner spring washers 64, form the ends of the friction spring assembly.
  • gaps 69 remain between the shoulders of the outer spring rings 60 and gaps 70 between the shoulders of the inner spring rings 64. The sum of the gap distances represents the maximum spring travel of the friction spring assembly.
  • FIG. 1 is considered in more detail.
  • the two thrust crank drives 8, 16 are rigidly coupled via the shaft 5, the thrust crank drive 16 being designed such that, when switched on, the auxiliary switching point 18 always switches on first and switches the on resistor 19 into the current path.
  • the current path then leads from the power connection 12 via the flexible connection 20, the closed secondary switching point 18 and the on-resistance 19 to the deflection housing 6 and from there usually via a similar arrangement to a current outlet located on the other side of the high-voltage switch.
  • the secondary switch 18 opens again immediately, and the current path then leads from the power connection 12 via the closed main switch 10 directly to the deflection housing 6.
  • the switch-on movement course of the movable contact 17 of the secondary switching point 18 is to be explained on the basis of FIG. 2 and compared with that of the moving contact 9 of the main switching point 10.
  • the effective length for the movement of the movable contact 17 of the secondary switching point 18 in the thrust crank drive 16 is the center distance between the shaft 5 and the pivot pin 24. This length is considerably greater than the effective length of the rotary lever 7 provided for the movement of the main switching point 10. It proves to be advantageous to choose a gear ratio between the effective length of the rotary lever 7 and the effective length in the thrust crank drives 16 in the range of 1: (1.4 to 1.8).
  • the movable contact 17 of the secondary switching point 18 runs greater than 1: 1 in a counterclockwise direction in front of the moving contact 9 of the main switching point 10 due to the transmission ratio.
  • the spring element 26 initially holds the levers 15 and 25 together in a first stable position so that the push-through joint 23 is certainly not stretched.
  • the movable contact 17 of the secondary switching point 18 is first in the "on" position and closes the current path in which the on-resistance 19 is active.
  • the ratio 1: 1.5 is preferably selected, since it follows that the secondary switching point 18 switches on approximately 8 to 10 milliseconds before the main switching point 10. This time span is sufficient for most practical operating cases. However, it is easily possible to increase or decrease this time span by lengthening or shortening the lever 15 in the area between the pivot point 28 and the shaft 5, without other parts of the thrust crank drive 16 having to be changed.
  • the load duration of the switch-on resistor 19 is increased and this has the consequence that switch-on overvoltages in the network at the place of use of the high-voltage switch are reduced over a longer period of time and thus to smaller values.
  • networks which are designed in such a way that a high switch-on overvoltage cannot occur it suffices to dampen them during a shorter time, so that the switch-on resistor 19 must only act during a shorter time. If, in this case, the mechanics ensure that the switch-on resistor 19 is actually only loaded for a comparatively short time, it can be dimensioned to be correspondingly scarcer and cheaper.
  • FIG. 3 schematically shows the moment when the secondary switching point 18 is switched on.
  • the first impact ring 34 strikes the first sprung stop 36, which dampens the impact energy. Via the connecting rod 29, the further movement of the hinge pin 24 in the switch-on direction is blocked.
  • FIG. 4 shows the position of the push crank drive 16 when the high-voltage switch is definitely switched on.
  • the distance between the impact ring 34 and the stop 36 shows that the contacts 17, 21 of the secondary switching point 18 are disengaged.
  • the high-voltage switch starts to be switched off.
  • the lever 15 moves clockwise and the contact distance of the auxiliary switch 18 which has already been open increases. Only now does the main switch 10 open and interrupt the current path.
  • the push crank drive 16 reaches the position shown in FIG. 5. Up to this position, the spring element 26 holds the push-through joint 23 in the second stable position. After the second impact ring 35 strikes the sprung second stop 37, the further movement of the pivot pin 24 in the switch-off direction is blocked.
  • the lever 15 is moved clockwise by the drive of the high-voltage switch.
  • the push-through joint 23 is again stretched to the dead center and, after the dead center position has been exceeded, it tilts back into the first stable position as a result of the force originating from the spring element 26.
  • the movable contact 17 of the secondary switching point 18 is moved somewhat in the switch-on direction.
  • the lever 15 continues to move clockwise until it reaches the definite switch-off position shown in FIG. 2 and takes the movable contact 17 with it via the push-crank drive 16.
  • the second impact ring 35 no longer bears against the second stop 37 here.
  • a friction spring assembly as shown in FIG. 7, can advantageously be used where large impact energies have to be damped in the smallest space.
  • the outer spring washers 60 and the inner spring washers 64 are pushed onto one another and stretched or compressed, the gaps 69, 70 between the individual spring washers becoming smaller.
  • the chamfers 61 and 65 as well as 62 and 66 rub each other intensively, which means that a large part of the impact energy is converted into frictional heat.
  • Friction spring assemblies work down to -50 ° C without loss of performance and are therefore particularly well suited for high-voltage switches installed outdoors.
  • the area around the push-through joint 23 is particularly advantageously constructed symmetrically, since jamming of the arrangement is thus reliably avoided.
  • two levers 15 and two levers 22 are arranged in parallel and the spring element 26 is fastened between them.
  • a spring element 26 is attached to each side of a simple lever arrangement consisting of lever 15 and lever 22.
  • FIG. 8 shows a further embodiment of the push crank drive 16, in which, in addition to the push-through joint 23, a further push-through joint 80 which interacts with it is provided.
  • the push-through joint 23 has the lever 15, which is non-positively connected to the shaft 5, and a two-arm lever 82, which is directed to the connecting rod 29 with an arm 81.
  • the push-through joint 80 is formed by an arm 83 of the two-arm lever 82 and one which is articulated on the one hand
  • Compression spring element 84 which on the other hand is articulated to the shaft 5.
  • the compression spring element 84 has a housing part 86 with a central bore 87, the axis of which runs next to the shaft 5.
  • a spring assembly 89 which preferably contains friction springs, is supported against a shoulder 88 of the central bore 87 and is held on the opposite side by a disk 90 sliding in the central bore 87.
  • a flange 91 connected to the housing part 86 secures the disk 90 Screw 93, which extends through a bore in the disk 90 and can also be designed as a bolt, is screwed to a housing part 94 which slides telescopically in the central bore 87.
  • the housing part 94 has a receptacle 95 for a compression spring 96, the other side of which is supported against the housing part 86.
  • a sleeve-like part 97 of the housing part 86 guides the compression spring 96 inside.
  • the compression spring 96 can be pretensioned according to the operating requirements by means of the screw 93.
  • an eyelet 98 is incorporated on the side facing away from the compression spring 96, which enables the connection to the articulated joint 80 via a bolt.
  • the mode of operation of the variant of the thrust crank drive 16 shown in FIG. 8 is similar to that of the variant already described with reference to FIGS. 2 to 5.
  • the course of movement of the secondary switching point 18 is identical in both variants in the areas essential for the proper functioning of the high-voltage switch. Differences only exist in the area around the respective dead center of the push crank drive 16, since in the variant according to FIG. 8 the actual dead center is only reached after the pushable joint 23 has been stretched, namely only when the pushable joint 80 is stretched.
  • the overturning of the thrust crank drive 16 can therefore only take place after the longitudinal axis of the central bore 87 of the compression spring element 84 and the connecting line between the centers of the two pressable joints 23 and 80 run parallel.
  • the last-described variant is characterized in particular by the fact that mechanical vibrations which arise from the respective end position when the thrust crank drive 16 starts to run can be damped quickly. In this way, absolutely reliable operating behavior of the push crank drive 16 can be achieved with a comparatively low-mass compression spring 96. Furthermore, it has an advantageous effect that, due to the low-mass compression spring 96, the reaction forces on the two push-through joints 23 and 80 and the other bearing points are also reduced, which results in an increase in the service life of the arrangement or enables a more economical construction.

Landscapes

  • Driving Mechanisms And Operating Circuits Of Arc-Extinguishing High-Tension Switches (AREA)

Description

Die vorliegende Erfindung betrifft einen Hochspannungsschalter mit Einschaltwiderstand gemäss dem Oberbegriff des Anspruchs 1.The present invention relates to a high-voltage switch with on-resistance according to the preamble of claim 1.

Aus der Offenlegungsschrift DE-A-3 132 821 ist bereits ein Hochspannungsschalter bekannt, bei welchem parallel zu einer Hauptschaltstelle die Serieschaltung einer Nebenschaltstelle mit einem Einschaltwiderstand liegt. Die Hauptschaltstelle wird über ein ihr zugeordnetes Hebelgetriebe betätigt, während ein weiteres Hebelgetriebe auf einen beweglichen Kontakt der Nebenschaltstelle wirkt. Das der Nebenschaltstelle zugeordnete Hebelgetriebe ist derart ausgebildet, dass die Nebenschaltstelle beim Einschalten immer vor der Hauptschaltstelle schliesst und dann nach dem Schliessen der Hauptschaltstelle wieder öffnet.A high-voltage switch is already known from the published patent application DE-A-3 132 821, in which the series connection of a secondary connection point with an on-resistance is connected in parallel with a main switching point. The main switching point is actuated via a lever gear assigned to it, while another lever gear acts on a movable contact of the secondary switching point. The lever gear assigned to the secondary switching point is designed such that the secondary switching point always closes before the main switching point when it is switched on and then opens again after the main switching point has been closed.

Um diesen Bewegungsablauf der Nebenschaltstelle zu erreichen, ist im zugeordneten Hebelgetriebe eine Vielzahl von Teilen nötig, welche nur geringe Fertigungstoleranzen aufweisen dürfen, da nur so ein Klemmen des Hebelgetriebes ausgeschlossen werden kann. Derart genau gefertigte Teile sind teuer.In order to achieve this sequence of movements of the secondary switching point, a large number of parts are required in the associated lever gear, which may only have small manufacturing tolerances, since this is the only way to prevent the lever gear from jamming. Parts manufactured in this way are expensive.

Hier will die Erfindung Abhilfe schaffen. Die Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, löst die Aufgabe, bei einem gattungsgemässen Hochspannungsschalter einen Bewegungsablauf zu erzielen, welcher sich unter Einsparung von Bauteilen des Antriebs in einfacher Weise an unterschiedliche Netzbedingungen anpassen lässt.The invention seeks to remedy this. The invention, as characterized in the claims, solves the task of achieving a movement sequence in a generic high-voltage switch, which can be adapted to different network conditions in a simple manner while saving on components of the drive.

Die durch die Erfindung erreichten Vorteile sind im wesentlichen darin zu sehen, dass einfacher ausgebildete und damit wirtschaftlichere Antriebsteile verwendet werden können. Die stets möglichen Fertigungstoleranzen fallen hier wenig ins Gewicht. Ferner ist es leicht möglich, durch Abänderung nur eines Teiles den Bewegungsablauf der Nebenschaltstelle zu modifizieren, so dass der Hochspannungsschalter auf diese Art unterschiedlichen Netzbedingungen angepasst werden kann.The advantages achieved by the invention can be seen essentially in the fact that simpler and thus more economical drive parts can be used. The manufacturing tolerances that are always possible are of little importance here. Furthermore, it is easily possible to modify the movement sequence of the secondary switching point by modifying only a part, so that the high-voltage switch can be adapted to different network conditions in this way.

Die weiteren Ausgestaltungen der Erfindung sind Gegenstände der abhängigen Ansprüche.The further developments of the invention are the subject of the dependent claims.

Im folgenden wird die Erfindung anhand von lediglich einen Ausführungsweg darstellenden Zeichnungen näher erläutert.The invention is explained in more detail below with the aid of drawings which illustrate only one embodiment.

Es zeigt:

  • Fig. 1 die schematische Darstellung einer ersten Ausführungsform eines erfindungsgemässen Hochspannungsschalters,
  • Fig. 2 einen Schnitt durch den Antriebsbereich der Nebenschaltstelle im definitiv ausgeschalteten Zustand des Hochspannungsschalters gemäss Fig. 1, wobei die Antriebselemente der Hauptschaltstelle gestrichelt eingezeichnet sind,
  • Fig. 3 einen stark vereinfachten Schnitt durch den in Fig. 2 dargestellten Antriebsbereich der Nebenschaltstelle, wobei der bewegliche Kontakt der Nebenschaltstelle eingeschaltet ist,
  • Fig. 4 einen stark vereinfachten Schnitt durch den in Fig. 2 dargestellten Antriebsbereich der Nebenschaltstelle bei definitiv eingeschaltetem Hochspannungsschalter,
  • 5. einen stark vereinfachten Schnitt durch den in Fig. 2 dargestellten Antriebsbereich der Nebenschaltstelle in dem Moment, in dem deren beweglicher Kontakt maximal geöffnet ist,
  • Fig. 6 einen Schnitt durch ein Federelement des in Fig. 2 gezeigten Antriebsbereiches,
  • Fig. 7 einen Schnitt durch eine Reibungsfederanordnung des in Fig. 2 gezeigten Antriebsbereiches, und
  • Fig. 8 einen Schnitt durch einen Teil des Antriebsbereiches einer Nebenschaltstelle im definitiv eingeschalteten Zustand einer zweiten Ausführungsform des erfindungsgemässen Hochspannungsschalters.
It shows:
  • 1 is a schematic representation of a first embodiment of a high-voltage switch according to the invention,
  • 2 shows a section through the drive area of the secondary switching point when the high-voltage switch according to FIG. 1 is definitely switched off, the drive elements of the main switching point being shown in dashed lines,
  • 3 shows a greatly simplified section through the drive area of the secondary switching point shown in FIG. 2, the movable contact of the secondary switching point being switched on,
  • 4 shows a greatly simplified section through the drive area of the secondary switching point shown in FIG. 2 when the high-voltage switch is definitely switched on,
  • 5. a greatly simplified section through the drive area of the secondary switching point shown in FIG. 2 at the moment when its movable contact is opened to the maximum,
  • 6 shows a section through a spring element of the drive area shown in FIG. 2,
  • FIG. 7 shows a section through a friction spring arrangement of the drive region shown in FIG. 2, and
  • 8 shows a section through part of the drive region of a secondary switching point in the definitely switched-on state of a second embodiment of the high-voltage switch according to the invention.

Bei allen Figuren sind gleich wirkende Teile mit gleichen Bezugszeichen versehen.Parts with the same effect are provided with the same reference symbols in all the figures.

In Figur 1 bewegt ein Antrieb 1 über eine durch eine Isolatorsäule 2 hindurchgeführte isolierende Antriebsstange 3 und über eine Hebelanordnung 4 eine Welle 5. Die Welle 5 ist in einem nur andeutungsweise dargestellten, leitenden Umlenkgehäuse 6 gelagert, welches sich auf die Isolatorsäule 2 abstützt. Ein an der Welle 5 kraftschlüssig befestigter Drehhebel 7 wirkt über einen ersten Schubkurbelantrieb 8 auf einen beweglichen Kontakt 9 einer Hauptschaltstelle 10 ein. Der bewegliche Kontakt 9 arbeitet mit einem festen Kontakt 11 zusammen, welcher mit einem Stromanschluss 12 verbunden ist. Ein an der Welle 5 kraftschlüssig befestigter Hebel 15 bewegt über einen zweiten Schubkurbelantrieb 16 einen beweglichen Kontakt 17 einer Nebenschaltstelle 18. Die Nebenschaltstelle 18 ist elektrisch in Serie geschaltet mit einem Einschaltwiderstand 19, und diese Serienschaltung liegt parallel zur Hauptschaltstelle 10. Eine flexible, leitende Verbindung 20 zwischen dem Stromanschluss 12 und einem festen Kontakt 21 der Nebenschaltstelle 18 stellt eine Parallelverbindung dar, während die andere Parallelverbindung durch das Umlenkgehäuse 6 gebildet wird. Die Hauptschaltstelle 10 und die Serieschaltung von Nebenschaltstelle 18 und Einschaltwiderstand 19 sind von nicht dargestellten Isoliergehäusen umgeben.In FIG. 1, a drive 1 moves via an insulating drive rod 3 which is guided through an insulator column 2 and a shaft 5 via a lever arrangement 4. The shaft 5 is mounted in a conductive deflection housing 6, which is only indicated and which is supported on the insulator column 2. A rotary lever 7 which is non-positively fastened to the shaft 5 acts on a movable contact 9 of a main switching point 10 via a first thrust crank drive 8. The movable contact 9 cooperates with a fixed contact 11 which is connected to a power connection 12. A lever 15, which is non-positively fastened to the shaft 5, moves a movable contact 17 of a secondary switching point 18 via a second thrust crank drive 16. The secondary switching point 18 is electrically connected in series with an on-resistance 19, and this series connection is parallel to the main switching point 10. A flexible, conductive connection 20 between the power connection 12 and a fixed contact 21 of the secondary switching point 18 represents a parallel connection, while the other parallel connection is formed by the deflection housing 6. The main switching point 10 and the series connection of secondary switching point 18 and switch-on resistor 19 are surrounded by insulating housings, not shown.

Figur 2 zeigt den Antriebsbereich der Nebenschaltstelle 18 bei definitiv ausgeschaltetem Hochspannungsschalter. Der Hebel 15 bildet mit einem angelenkten Hebel 22 ein durchdrückbares Gelenk 23. Das dem Hebel 15 abgewandte Ende des Hebels 22 umfasst einen Gelenkbolzen 24 und ist über diesen mit einer ersten Halterung 25 eines Federelementes 26 verbunden. Eine zweite Halterung 27 des Federelementes 26 ist mit einem, auf dem Hebel 15 benachbart zur Welle 5 angeordneten Drehpunkt 28 verbunden. Ferner ist an dem Gelenkbolzen 24 das eine Ende einer Pleuelstange 29 angelenkt, deren anderes Ende gelenkig mit einem Führungsstück 30 verbunden ist. Dieses Führungsstück 30 gleitet in einer mit dem Umlenkgehäuse 6 über Rippen 31 verbundenen zylindrischen Hülse 32 und ist starr mit dem einen Ende einer aus stab- oder rohrförmigem Isoliermaterial gefertigten Betätigungsstange 33 verbunden. Das andere Ende der Betätigungsstange 33 durchdringt die durchbohrten Scheiben des Einschaltwiderstandes 19 und ist mit dem beweglichen Kontakt 17 der Nebenschaltstelle 18 verbunden.FIG. 2 shows the drive area of the secondary switching point 18 when the high-voltage switch is definitely switched off. The lever 15 forms a push-through joint 23 with a hinged lever 22. The end of the lever 22 facing away from the lever 15 comprises a joint bolt 24 and is connected to a first holder 25 of a spring element 26. A second holder 27 of the spring element 26 is connected to a pivot point 28 arranged on the lever 15 adjacent to the shaft 5. Furthermore, one end of a connecting rod 29 is articulated on the hinge pin 24, the other end of which is articulated to a guide piece 30. This guide piece 30 slides in a cylindrical sleeve 32 connected to the deflection housing 6 via ribs 31 and is rigidly connected to the one end of an actuating rod 33 made of rod-shaped or tubular insulating material. The other end of the actuating rod 33 penetrates the pierced disks of the on-resistance 19 and is with connected to the movable contact 17 of the secondary switching point 18.

Auf der Betätigungsstange 33 sitzt ein erster Aufschlagring 34 fest, welcher sich zusätzlich auf das Führungsstück 30 abstützt. Ein zweiter Aufschlagring 35 ist ebenfalls starr auf der Betätigungsstange 33 befestigt. Im Bereich zwischen den Aufschlagringen 34, 35 umgeben zwei Anschläge 36, 37 konzentrisch die Betätigungsstange 33. Die beiden Anschläge 36, 37 stützen sich an einander entgegengesetzten Seiten auf ein gemeinsames, sie in axialer Richtung abfederndes zweiseitig beaufschlagbares Federpaket 38 ab und werden zusammen mit diesem von einer Halterung 39 getragen. Die Halterung 39 ist in der Hülse 32 starr befestigt.A first impact ring 34 is seated on the actuating rod 33 and is additionally supported on the guide piece 30. A second impact ring 35 is also rigidly attached to the operating rod 33. In the area between the impact rings 34, 35, two stops 36, 37 concentrically surround the actuating rod 33. The two stops 36, 37 are supported on opposite sides on a common spring assembly 38 which can cushion them in the axial direction and become together with this carried by a bracket 39. The bracket 39 is rigidly attached in the sleeve 32.

In Figur 6 ist ein Schnitt durch das Federelement 26 dargestellt. Jede der beiden Halterungen 25, 27 weist eine Oese 45 zur Befestigung auf und nimmt ein Ende einer Zugfeder 46 auf, welche die beiden Halterungen 25, 27 in axialer Richtung beaufschlagt. Die Halterung 25 umfasst die Halterung 27 teilweise und führt die Zugfeder 46. Die Halterung 27 trägt eine Dämpfungseinrichtung 47, welche mittels einer Halteschraube 48 befestigt ist. Die Halteschraube 48 hält eine Dämpferscheibe 49 so, dass diese in axialer Richtung entlang dem Schaft 48a derselben gleiten kann. Die Dämpferscheibe 49 wird einerseits von einer Schulter 50 der Halterung 25 mit der Federkraft der Zugfeder 46 beaufschlagt und andererseits stützt sie sich auf ein Federpaket 51 ab und drückt dieses gegen eine Schulter 52 der Halterung 27.FIG. 6 shows a section through the spring element 26. Each of the two brackets 25, 27 has an eyelet 45 for attachment and receives one end of a tension spring 46 which acts on the two brackets 25, 27 in the axial direction. The bracket 25 partially includes the bracket 27 and guides the tension spring 46. The bracket 27 carries a damping device 47 which is fastened by means of a retaining screw 48. The retaining screw 48 holds a damper disk 49 so that it can slide in the axial direction along the shaft 48a thereof. The damper disk 49 is acted upon on the one hand by a shoulder 50 of the holder 25 with the spring force of the tension spring 46 and on the other hand it is supported on a spring assembly 51 and presses it against a shoulder 52 of the holder 27.

In Figur 7 ist ein zylindrisch aufgebautes Reibungsfederpaket schematisch dargestellt, wie es z.B. in den Anordnungen entsprechend Figur 2 (Federpaket 38) und Figur 6 (Federpaket 51) zwischen kraftübertragenden Teilen, wie etwa den beiden Anschlägen 36, 37, eingebaut werden kann. Das Reibungsfederpaket bestehet aus Aussenfederringen 60 und Innenfederringen 64, welche abwechslungsweise aufeinandergestapelt sind. Jeder Aussenfederring 60 weist innen konische Anfasungen 61, 62 auf, die von beiden Seiten gleichartig ausgeführt sind und die sich in einer Kante 63 treffen. Jeder Innenfederring 64 weist aussen konische Anfasungen 65, 66 auf, welche von beiden Seiten gleichartig ausgeführt sind und die sich in einer Kante 67 treffen. Die Anfasungen 61 und 65 sowie 62 und 66 passen beim Stapeln des Reibungsfederpaketes genau aufeinander. Endringe 68, welche halbierten Innenfederringen 64 entsprechen, bilden die Enden des Reibungsfederpaketes. Beim Stapeln der Federringe bleiben zwischen den Schultern der Aussenfederringe 60 Spalte 69 und zwischen den Schultern der Innenfederringe 64 Spalte 70. Die Summe der Spaltabstände stellt den maximalen Federweg des Reibungsfederpaketes dar.In Figure 7, a cylindrical friction spring assembly is shown schematically, such as e.g. in the arrangements according to FIG. 2 (spring assembly 38) and FIG. 6 (spring assembly 51) between force-transmitting parts, such as the two stops 36, 37, can be installed. The friction spring assembly consists of outer spring rings 60 and inner spring rings 64, which are alternately stacked on top of one another. Each outer spring ring 60 has conical bevels 61, 62 on the inside, which are designed identically from both sides and which meet in an edge 63. Each inner spring ring 64 has conical chamfers 65, 66 on the outside, which are of identical design from both sides and which meet in an edge 67. The chamfers 61 and 65 as well as 62 and 66 match each other exactly when the friction spring assembly is stacked. End rings 68, which correspond to halved inner spring washers 64, form the ends of the friction spring assembly. When the spring rings are stacked, gaps 69 remain between the shoulders of the outer spring rings 60 and gaps 70 between the shoulders of the inner spring rings 64. The sum of the gap distances represents the maximum spring travel of the friction spring assembly.

Zur Erläuterung der Wirkungsweise sei die Figur 1 näher betrachtet. Ueber die Welle 5 sind die beiden Schubkurbelantriebe 8, 16 starr gekoppelt, wobei der Schubkurbelantrieb 16 so ausgelegt ist, dass bei einer Einschaltung stets zuerst die Nebenschaltstelle 18 einschaltet und den Einschaltwiderstand 19 in den Strompfad schaltet. Der Strompfad führt dann vom Stromanschluss 12 über die flexible Verbindung 20, die geschlossene Nebenschaltstelle 18 und den Einschaltwiderstand 19 auf das Umlenkgehäuse 6 und von dort in der Regel weiter über eine gleichartige Anordnung auf einen, auf der anderen Seite des Hochspannungsschalters gelegenen Stromabgang. Nach dem Schliessen der Hauptschaltstelle 10 geht die Neben schaltstelle 18 sofort wieder auf, und der Strompfad führt dann vom Stromanschluss 12 über die geschlossene Hauptschaltstelle 10 direkt auf das Umlenkgehäuse 6.To explain the mode of operation, FIG. 1 is considered in more detail. The two thrust crank drives 8, 16 are rigidly coupled via the shaft 5, the thrust crank drive 16 being designed such that, when switched on, the auxiliary switching point 18 always switches on first and switches the on resistor 19 into the current path. The current path then leads from the power connection 12 via the flexible connection 20, the closed secondary switching point 18 and the on-resistance 19 to the deflection housing 6 and from there usually via a similar arrangement to a current outlet located on the other side of the high-voltage switch. After the main switch 10 is closed, the secondary switch 18 opens again immediately, and the current path then leads from the power connection 12 via the closed main switch 10 directly to the deflection housing 6.

Anhand von Figur 2 soll der Einschaltbewegungsverlauf des beweglichen Kontaktes 17 der Nebenschaltstelle 18 erläutert und mit dem des beweglichen Kontaktes 9 der Hauptschaltstelle 10 verglichen werden. Die für die Bewegung des beweglichen Kontaktes 17 der Nebenschaltstelle 18 wirksame Länge im Schubkurbelantrieb 16 ist der Achsabstand zwischen Welle 5 und Gelenkbolzen 24. Diese Länge ist wesentlich grösser als die wirksame Länge des für die Bewegung der Hauptschaltstelle 10 vorgesehenen Drehhebels 7. Es erweist sich als vorteilhaft, ein Uebersetzungsverhältnis zwischen wirksamer Länge des Drehhebels 7 und wirksamer Länge im Schubkurbelantriebe 16 im Bereich von 1 : (1,4 bis 1,8) zu wählen.The switch-on movement course of the movable contact 17 of the secondary switching point 18 is to be explained on the basis of FIG. 2 and compared with that of the moving contact 9 of the main switching point 10. The effective length for the movement of the movable contact 17 of the secondary switching point 18 in the thrust crank drive 16 is the center distance between the shaft 5 and the pivot pin 24. This length is considerably greater than the effective length of the rotary lever 7 provided for the movement of the main switching point 10. It proves to be advantageous to choose a gear ratio between the effective length of the rotary lever 7 and the effective length in the thrust crank drives 16 in the range of 1: (1.4 to 1.8).

Sobald der Einschaltvorgang, ausgehend von der in Figur 2 dargestellten Stellung des Schubkurbelantriebs 16, beginnt, läuft der bewegliche Kontakt 17 der Nebenschaltstelle 18 infolge des Uebersetzungsverhältnisses grösser als 1 : 1 im Gegenuhrzeigersinn vor dem beweglichen Kontakt 9 der Hauptschaltstelle 10 her. Das Federelement 26 hält die Hebel 15 und 25 zunächst in einer ersten stabilen Lage so zusammen, dass das durchdrückbare Gelenk 23 sicher nicht gestreckt wird. Der bewegliche Kontakt 17 der Nebenschaltstelle 18 ist zuerst in "Ein"-Stellung und schliesst den Strompfad, in welchem der Einschaltwiderstand 19 wirksam ist.As soon as the switch-on process begins, starting from the position of the thrust crank drive 16 shown in FIG. 2, the movable contact 17 of the secondary switching point 18 runs greater than 1: 1 in a counterclockwise direction in front of the moving contact 9 of the main switching point 10 due to the transmission ratio. The spring element 26 initially holds the levers 15 and 25 together in a first stable position so that the push-through joint 23 is certainly not stretched. The movable contact 17 of the secondary switching point 18 is first in the "on" position and closes the current path in which the on-resistance 19 is active.

Vorzugsweise wird das Uebersetzungsverhältnis 1 : 1,5 gewählt, denn daraus ergibt sich, dass die Nebenschaltstelle 18 rund 8 bis 10 Millisekunden vor der Hauptschaltstelle 10 einschaltet. Diese Zeitspanne genügt für die meisten praktischen Betriebsfälle. Es ist jedoch leicht möglich durch Verlängern bzw. Verkürzen des Hebels 15 im Bereich zwischen dem Drehpunkt 28 und der Welle 5 diese Zeitspanne zu vergrössern bzw. zu verkleinern, ohne dass sonstige Teile des Schubkurbelantriebes 16 abgeändert werden müssen.The ratio 1: 1.5 is preferably selected, since it follows that the secondary switching point 18 switches on approximately 8 to 10 milliseconds before the main switching point 10. This time span is sufficient for most practical operating cases. However, it is easily possible to increase or decrease this time span by lengthening or shortening the lever 15 in the area between the pivot point 28 and the shaft 5, without other parts of the thrust crank drive 16 having to be changed.

Durch das Vergrössern der Zeitspanne wird die Belastungsdauer des Einschaltwiderstandes 19 vergrössert und dies hat zur Folge, dass Einschalt- überspannungen im Netz am Einsatzort des Hochspannungsschalters während längerer Zeit und damit auf kleinere Werte abgebaut werden. In Netzen, die so konzipiert sind, dass keine hohen Einschalt- überspannung auftreten können, genugt es, diese während kürzerer Zeit zu dämpfen, so dass der Einschaltwiderstand 19 nut während kürzerer Zeit wirken muss. Wird in diesem Fall von der Mechanik her sichergestellt, dass der Einschaltwiderstand 19 tatsächlich nur vergleichsweise kurz belastet wird, so kann er entsprechend knapper dimensioniert und billiger ausgeführt werden.By increasing the time span, the load duration of the switch-on resistor 19 is increased and this has the consequence that switch-on overvoltages in the network at the place of use of the high-voltage switch are reduced over a longer period of time and thus to smaller values. In networks which are designed in such a way that a high switch-on overvoltage cannot occur, it suffices to dampen them during a shorter time, so that the switch-on resistor 19 must only act during a shorter time. If, in this case, the mechanics ensure that the switch-on resistor 19 is actually only loaded for a comparatively short time, it can be dimensioned to be correspondingly scarcer and cheaper.

Figur 3 zeigt schematisch den Moment des Einschaltens der Nebenschaltstelle 18. Der erste Aufschlagring 34 schlägt auf den ersten abgefederten Anschlag 36 auf, welcher die Auftreffenergie dämpft. Ueber die Pleuelstange 29 wird die weitere Bewegung des Gelenkbolzens 24 in Einschaltrichtung blockiert.FIG. 3 schematically shows the moment when the secondary switching point 18 is switched on. The first impact ring 34 strikes the first sprung stop 36, which dampens the impact energy. Via the connecting rod 29, the further movement of the hinge pin 24 in the switch-on direction is blocked.

Der Hebel 15 wird jedoch vom Antrieb des Hochspannungsschalters im Gegenuhrzeigersinn weiterbewegt. Das durchdrückbare Gelenk 23 wird infolgedessen gegen die Federkraft des Federelementes 26 gestreckt. Dieser Streckvorgang geht weiter bis zu einem Totpunkt, der dadurch gekennzeichnet ist, dass die Achsen des Drehpunktes 28, des durchdrückbaren Gelenks 23 und des Gelenkbolzens 24 in einer Ebene liegen. Kurz vor dem Erreichen dieses Totpunktes hat die Hauptschaltstelle 10 ebenfalls einge schaltet und der Strom fliesst jetzt über diese Schaltstelle.However, the lever 15 is moved further by the drive of the high-voltage switch in the counterclockwise direction. The push-through joint 23 is consequently stretched against the spring force of the spring element 26. This stretching process continues to a dead center, which is characterized in that the axes of the pivot point 28, the push-through joint 23 and the joint bolt 24 lie in one plane. Shortly before reaching this dead center, the main switching point 10 also switched on and the current now flows through this switching point.

Nach dem Ueberschreiten der Totpunktlage kippt, angetrieben durch die Federkraft des Federelementes 26, das durchdrückbare Gelenk 23 in eine zweite stabile Lage um. Durch dieses Umkippen wird auf die Pleuelstange 29 eine Kraft in Ausschaltrichtung wirksam, welche die Nebenschaltstelle 18 öffnet. Der Hebel 15 bewegt sich danach noch etwas im Gegenuhrzeigersinn weiter bis zum definitiven Abschluss des Einschaltvorganges. Figur 4 zeigt die Stellung des Schubkurbelantriebs 16 bei definitiv eingeschaltetem Hochspannungsschalter. Der Abstand zwischen Aufschlagring 34 und Anschlag 36 zeigt, dass die Kontakte 17, 21 der Nebenschaltstelle 18 ausser Eingriff sind.After the dead center position has been exceeded, driven by the spring force of the spring element 26, the articulated joint 23 tilts into a second stable position. As a result of this overturning, a force acts in the disconnection direction on the connecting rod 29, which force opens the secondary switching point 18. The lever 15 then moves a little counterclockwise until the switch-on process is finally completed. FIG. 4 shows the position of the push crank drive 16 when the high-voltage switch is definitely switched on. The distance between the impact ring 34 and the stop 36 shows that the contacts 17, 21 of the secondary switching point 18 are disengaged.

Ausgehend von der in Figur 4 dargestellten Stellung des Schubkurbelantriebs 16 beginnt der Ausschaltvorgang des Hochspannungsschalters. Der Hebel 15 bewegt sich im Uhrzeigersinn und der Kontaktabstand der bereits offen gewesenen Nebenschaltstelle 18 nimmt zu. Erst jetzt öffnet sich die Hauptschaltstelle 10 und unterbricht den Strompfad. Die beim Ausschalten ebenfalls aufgrund des Uebersetzungsverhältnisses grösser als 1 : 1 der Hauptschaltstelle 10 vorlaufende Nebenschaltstelle 18 weist so stets eine grössere Spannungsfestigkeit auf als die Hauptschaltstelle.Starting from the position of the thrust crank drive 16 shown in FIG. 4, the high-voltage switch starts to be switched off. The lever 15 moves clockwise and the contact distance of the auxiliary switch 18 which has already been open increases. Only now does the main switch 10 open and interrupt the current path. The secondary switching point 18, which also moves forward due to the transmission ratio greater than 1: 1 of the main switching point 10, always has a greater dielectric strength than the main switching point.

Gegen Ende der Ausschaltbewegung erreicht der Schubkurbelantrieb 16 die in Figur 5 gezeigte Stellung. Bis zu dieser Stellung hält das Federelement 26 das durchdrückbare Gelenk 23 in der zweiten stabilen Lage. Nach dem Aufschlagen des zweiten Aufschlagringes 35 auf den abgefederten zweiten Anschlag 37 wird die weitere Bewegung des Gelenkbolzens 24 in Ausschaltrichtung blockiert.Towards the end of the switch-off movement, the push crank drive 16 reaches the position shown in FIG. 5. Up to this position, the spring element 26 holds the push-through joint 23 in the second stable position. After the second impact ring 35 strikes the sprung second stop 37, the further movement of the pivot pin 24 in the switch-off direction is blocked.

Der Hebel 15 wird jedoch vom Antrieb des Hochspannungsschalters im Uhrzeigersinn weiterbewegt. Das durchdrückbare Gelenk 23 wird infolgedessen wieder bis zum Totpunkt gestreckt und nach dem Ueberschreiten der Totpunktlage kippt es, infolge der vom Federelement 26 herrührenden Kraft, wieder in die erste stabile Lage zurück. Als Folge dieses Umkippens wird der bewegliche Kontakt 17 der Nebenschaltstelle 18 etwas in Einschaltrichtung bewegt. Der Hebel 15 bewegt sich jedoch im Uhrzeigersinn weiter, bis er die in Figur 2 dargestellte definitive Ausschaltstellung erreicht, und nimmt über den Schubkurbelantrieb 16 den beweglichen Kontakt 17 mit. Infolge des Umkippens liegt auch hier der zweite Aufschlagring 35 nicht mehr an dem zweiten Anschlag 37 an.However, the lever 15 is moved clockwise by the drive of the high-voltage switch. As a result, the push-through joint 23 is again stretched to the dead center and, after the dead center position has been exceeded, it tilts back into the first stable position as a result of the force originating from the spring element 26. As a result of this overturning, the movable contact 17 of the secondary switching point 18 is moved somewhat in the switch-on direction. However, the lever 15 continues to move clockwise until it reaches the definite switch-off position shown in FIG. 2 and takes the movable contact 17 with it via the push-crank drive 16. As a result of the overturning, the second impact ring 35 no longer bears against the second stop 37 here.

Die Funktion des Federelementes 26 soll anhand der Figur 6 erläutert werden. Wird die Zugfeder 46 durch an den beiden Oesen 45 in entgegengesetzter Richtung wirkende Kräfte gedehnt, so hebt sich die Schulter 50 von der Dämpferscheibe 49 ab. Wird nun die Zugfeder plötzlich entlastet, wie dies jeweils nach dem Umkippen des durchdrückbaren Gelenkes 23 erfolgt, so schlägt die Schulter 50 auf die Dämpfungsscheibe 49 auf, wobei die Kraft der Zugfeder 46 für die Aufschlagenergie massgebend ist. Die Aufschlagenergie wird durch das Federpaket 51 abgedämpft, so dass die beiden Halterungen 25, 27 vor mechanischer Ueberbeanspruchung geschützt werden.The function of the spring element 26 will be explained with reference to Figure 6. If the tension spring 46 is stretched by forces acting in opposite directions on the two eyelets 45, the shoulder 50 lifts off the damper disk 49. If the tension spring is suddenly relieved, as is done after the articulated joint 23 tilts over, the shoulder 50 strikes the damping disk 49, the force of the tension spring 46 determining the impact energy. The impact energy is dampened by the spring assembly 51, so that the two brackets 25, 27 are protected against mechanical overload.

Ein Reibungsfederpaket, wie in Figur 7 dargestellt, lässt sich vorteilhaft dort einsetzen, wo grosse Aufschlagenergien auf kleinstem Raum abgedämpft werden müssen. Bei mechanischer Belastung der Anschläge 36, 37 in axialer Richtung, werden die Aussenfederringe 60 und die Innenfederringe 64 aufeinandergeschoben und gedehnt bzw. zusammengedrückt, dabei verkleinern sich die Spalte 69, 70 zwischen den einzelnen Federringen. Die Anfasungen 61 und 65 sowie 62 und 66 reiben intensiv aufeinander, dadurch wird ein grosser Teil der Aufschlagenergie in Reibungswärme umgesetzt. Reibungsfederpakete arbeiten bis -50 °C ohne Leistungseinbusse und sind deshalb für im Freien aufgestellte Hochspannungsschalter besonders gut geeignet.A friction spring assembly, as shown in FIG. 7, can advantageously be used where large impact energies have to be damped in the smallest space. With mechanical loading of the stops 36, 37 in the axial direction, the outer spring washers 60 and the inner spring washers 64 are pushed onto one another and stretched or compressed, the gaps 69, 70 between the individual spring washers becoming smaller. The chamfers 61 and 65 as well as 62 and 66 rub each other intensively, which means that a large part of the impact energy is converted into frictional heat. Friction spring assemblies work down to -50 ° C without loss of performance and are therefore particularly well suited for high-voltage switches installed outdoors.

Besonders vorteilhaft wird der Bereich um das durchdrückbare Gelenk 23 symmetrisch aufgebaut, da so ein Klemmen der Anordnung sicher vermieden wird. Bei einer ersten konstruktiven Ausführung werden zwei Hebel 15 und zwei Hebel 22 parallel angeordnet und zwischen ihnen wird das Federelement 26 befestigt. Bei einer zweiten konstruktiven Ausführung wird an jeder Seite einer einfachen Hebelanordnung bestehend aus Hebel 15 und Hebel 22 ein Federelement 26 angebracht.The area around the push-through joint 23 is particularly advantageously constructed symmetrically, since jamming of the arrangement is thus reliably avoided. In a first constructive embodiment, two levers 15 and two levers 22 are arranged in parallel and the spring element 26 is fastened between them. In a second design, a spring element 26 is attached to each side of a simple lever arrangement consisting of lever 15 and lever 22.

Aus Fig. 8 ist eine weitere Ausführungsform des Schubkurbelantriebs 16 ersichtlich, bei welcher neben dem durchdrückbaren Gelenk 23 ein weiteres, mit diesem zusammenwirkendes durchdrückbares Gelenk 80 vorgesehen ist. Das durchdrückbare Gelenk 23 weist den mit der Welle 5 kraftschlüssig verbundenen Hebel 15 auf und einen mit einem Arm 81 an die Pleuelstange 29 gelenkten zweiarmigen Hebel 82. Das durchdrückbare Gelenk 80 wird gebildet durch einen Arm 83 des zweiarmigen Hebels 82 und ein einerseits an diesen angelenktes Druckfederelement 84, welches andererseits an die Welle 5 angelenkt ist. Das Druckfederelement 84 weist ein Gehäuseteil 86 mit einer zentralen Bohrung 87 auf, deren Achse neben der Welle 5 verläuft. Gegen eine Schulter 88 der zentralen Bohrung 87 stützt sich ein vorzugsweise Reibungsfedern enthaltendes Federpaket 89 ab, welches auf der Gegenseite durch eine in der zentralen Bohrung 87 gleitende Scheibe 90 gehalten wird. Ein mit dem Gehäuseteil 86 verbundener Flansch 91 sichert die Scheibe 90. Eine sich durch eine Bohrung der Scheibe 90 erstreckende Schraube 93, die auch als Bolzen ausgebildet sein kann, ist mit einem in der zentralen Bohrung 87 teleskopartig gleitenden Gehäuseteil 94 verschraubt. Das Gehäuseteil 94 weist eine Aufnahme 95 auf für eine Druckfeder 96, deren andere Seite sich gegen das Gehäuseteil 86 abstützt. Ein hülsenartig ausgebildeter Teil 97 des Gehäuseteiles 86 führt die Druckfeder 96 innen. Mittels der Schraube 93 kann die Druckfeder 96 entsprechend den Betriebsanforderungen vorgespannt werden. Im Gehäuseteil 94 ist auf der der Druckfeder 96 abgewandten Seite eine Oese 98 eingearbeitet, welche über einen Bolzen die Verbindung zum durchdrückbaren Gelenk 80 ermöglicht.8 shows a further embodiment of the push crank drive 16, in which, in addition to the push-through joint 23, a further push-through joint 80 which interacts with it is provided. The push-through joint 23 has the lever 15, which is non-positively connected to the shaft 5, and a two-arm lever 82, which is directed to the connecting rod 29 with an arm 81. The push-through joint 80 is formed by an arm 83 of the two-arm lever 82 and one which is articulated on the one hand Compression spring element 84, which on the other hand is articulated to the shaft 5. The compression spring element 84 has a housing part 86 with a central bore 87, the axis of which runs next to the shaft 5. A spring assembly 89, which preferably contains friction springs, is supported against a shoulder 88 of the central bore 87 and is held on the opposite side by a disk 90 sliding in the central bore 87. A flange 91 connected to the housing part 86 secures the disk 90 Screw 93, which extends through a bore in the disk 90 and can also be designed as a bolt, is screwed to a housing part 94 which slides telescopically in the central bore 87. The housing part 94 has a receptacle 95 for a compression spring 96, the other side of which is supported against the housing part 86. A sleeve-like part 97 of the housing part 86 guides the compression spring 96 inside. The compression spring 96 can be pretensioned according to the operating requirements by means of the screw 93. In the housing part 94, an eyelet 98 is incorporated on the side facing away from the compression spring 96, which enables the connection to the articulated joint 80 via a bolt.

Auch bei dieser Ausführungsform wirkt es sich vorteilhaft aus, wenn das Druckfederelement 84 zwischen jeweils zwei parallel angeordneten Hebeln 15 und 82 angeordnet wird, da so ein Verkanten des Schubkurbelantriebs 16 und eine einseitige Abnutzung der Lagerstellen mit Sicherheit vermieden wird.It also has an advantageous effect in this embodiment if the compression spring element 84 is arranged between two levers 15 and 82 arranged in parallel, since tilting of the thrust crank drive 16 and one-sided wear of the bearing points are avoided with certainty.

Die Wirkungsweise der in Fig. 8 dargestellten Variante des Schubkurbelantriebs 16 ist ähnlich wie die der bereits anhand von Fig. 2 bis Fig. 5 beschriebenen Ausführungsvariante. Der Bewegungsverlauf der Nebenschaltstelle 18 ist bei beiden Varianten in den für das einwandfreie Funktionieren des Hochspannungsschalters wesentlichen Bereichen identisch. Lediglich im Bereich um den jeweiligen Totpunkt des Schubkurbelantriebs 16 bestehen Unterschiede, da bei der Variante entsprechend Fig. 8 der eigentliche Totpunkt erst nach der Streckung des durchdrückbaren Gelenkes 23 erreicht wird, nämlich erst dann, wenn das durchdrückbare Gelenk 80 gestreckt ist. Das Umkippen des Schubkurbelantriebes 16 kann also erst erfolgen, nachdem die Längsachse der zentralen Bohrung 87 des Druckfederelements 84 und die Verbindungslinie zwischen den Zentren der beiden durchdrückbaren Gelenke 23 und 80 parallel verlaufen.The mode of operation of the variant of the thrust crank drive 16 shown in FIG. 8 is similar to that of the variant already described with reference to FIGS. 2 to 5. The course of movement of the secondary switching point 18 is identical in both variants in the areas essential for the proper functioning of the high-voltage switch. Differences only exist in the area around the respective dead center of the push crank drive 16, since in the variant according to FIG. 8 the actual dead center is only reached after the pushable joint 23 has been stretched, namely only when the pushable joint 80 is stretched. The overturning of the thrust crank drive 16 can therefore only take place after the longitudinal axis of the central bore 87 of the compression spring element 84 and the connecting line between the centers of the two pressable joints 23 and 80 run parallel.

Die zuletzt geschilderte Variante zeichnet sich insbesondere dadurch aus, dass mechanische Schwingungen, die beim Loslaufen des Schubkurbelantriebs 16 aus der jeweiligen Endstellung entstehen, schnell abgedämpft werden können. Auf diese Art kann bereits mit einer vergleichsweise massearmen Druckfeder 96 ein absolut sicheres Betriebsverhalten des Schubkurbelantriebs 16 erreicht werden. Ferner wirkt es sich vorteilhaft aus, dass infolge der massearmen Druckfeder 96 auch die Reaktionskräfte auf die beiden durchdrückbaren Gelenke 23 und 80 und die übrigen Lagerstellen reduziert werden, was eine Erhöhung der Lebensdauer der Anordnung zur Folge hat, bzw. eine wirtschaftlichere Konstruktion ermöglicht.The last-described variant is characterized in particular by the fact that mechanical vibrations which arise from the respective end position when the thrust crank drive 16 starts to run can be damped quickly. In this way, absolutely reliable operating behavior of the push crank drive 16 can be achieved with a comparatively low-mass compression spring 96. Furthermore, it has an advantageous effect that, due to the low-mass compression spring 96, the reaction forces on the two push-through joints 23 and 80 and the other bearing points are also reduced, which results in an increase in the service life of the arrangement or enables a more economical construction.

Claims (11)

1. High-voltage switch with a switch-on resistor (19) and with at least one main switch point (10) and at least one secondary switch point (18), the at least one secondary switch point (18) being in series with the switch-on resistor (19) and this series connection being in parallel with the at least one main switch point (10), and a movable contact (9, 17) of the at least one main switch point (10) and of the at least one secondary switch point (18) being actuable respectively by a thrust-crank mechanism (8, 16) driven via a common shaft (5), with the at least one secondary switch point (18) always closing before the at least one main switch point (10) and opening again immediately after the closing of the at least one main switch point (10), characterized in that the thrust-crank mechanism (16) acting on the movable contact (17) of the secondary switch point (18) has a first reversible joint (23), and in that the movable contact (17) of the at least one secondary switch point (18) is coupled to two impact rings (34, 35) which interact with two stops (36, 37) in such a way that, after the first impact ring (34) strikes the first stop (36) when the secondary switch point (18) is cut in, the first reversible joint (23) is guided by the mechanism from a first stable position beyond a dead centre, and, after the second impact ring (35) strikes the second stop (37) towards the end of the cut-out operation, the first reversible joint (23) is guided by the mechanism from a second stable position beyond a dead centre.
2. High-voltage switch according to Claim 1, characterized in that the first stop (36) and the second stop (37) are made resilient in the axial direction, and in that the two stops (36, 37) are supported, on opposite sides to one another, on a common spring assembly (38) loadable on two sides.
3. High-voltage switch according to one of claims 1 or 2, characterized in that, in addition to the first reversible joint (23), there is at least one second reversible joint (80) interacting with the first (Figure 8).
4. High-voltage switch according to one of claims 1 or 2, characterized in that the first reversible joint (23) has at least one first lever (15) fastened non-positively to the shaft (5), at least one second lever (22) articulated on a connecting rod (29), and at least one spring element (26) which is articulated on the two levers (15, 22) (Figure 2).
5. High-voltage switch according to Claim 4, characterized in that the spring element (26) has a tension spring (46) and a damping device (47) with a spring assembly (51).
6. High-voltage switch according to Claim 5, characterized in that one end of the tension spring (46) is fastened by means of a first mounting (25) to a joint pin (24) which connects the second lever (22) to the connecting rod (29), and in that its other end is coupled by means of a second mounting (27) to a fulcrum (28) of the first lever (15) located adjacent to the shaft (5).
7. High-voltage switch according to Claim 6, characterized in that the first mounting (25) serves as a guide part for the tension spring (46) and partially surrounds the second mounting (27) which carries the spring assembly (51) of the damping device (47).
8. High-voltage switch according to Claim 3, characterized in that the first reversible joint (23) has at least one first lever (15) fastened non-positively to the shaft (5) and at least one two-armed lever (82) which is articulated on the first lever (15) and the first arm (81) of which is articulated on a connecting rod (29), and in that the second reversible joint (80) is formed by a second arm (83) of the at least one two-armed lever (82) and by a compression-spring element (84) which is articulated on the one hand on the latter and on the other hand on the shaft (5).
9. High-voltage switch according to Claim 8, characterized in that the compression-spring element (84) is formed by two housing parts (86, 94) sliding telescopically one in the other and by a compression spring (96) supported on the two housing parts (86, 94).
10. High-voltage switch according to Claim 9, characterized in that supported on one (86) of the housing parts (86, 94) is a spring assembly (89) which damps the movement of the other (94) of the housing parts.
11. High-voltage switch according to Claim 10, characterized in that the one housing part (86) supporting the spring assembly (89) has a displaceable disc (90) supported on the spring assembly (89) and having an orifice, through which is guided a pin connected non-positively to the other housing part (94) and interacting with the disc (90).
EP86103192A 1985-03-27 1986-03-10 High tension circuit breaker with closing resistor Expired EP0197339B1 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CH1338/85 1985-03-27
CH133885 1985-03-27
CH724/86 1986-02-24
CH72486 1986-02-24

Publications (2)

Publication Number Publication Date
EP0197339A1 EP0197339A1 (en) 1986-10-15
EP0197339B1 true EP0197339B1 (en) 1989-06-21

Family

ID=25685488

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86103192A Expired EP0197339B1 (en) 1985-03-27 1986-03-10 High tension circuit breaker with closing resistor

Country Status (4)

Country Link
US (1) US4670632A (en)
EP (1) EP0197339B1 (en)
BR (1) BR8601333A (en)
DE (1) DE3664077D1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE9103300L (en) * 1991-11-08 1993-03-29 Asea Brown Boveri Triple High Voltage Switch
DE19547098A1 (en) * 1995-12-16 1997-06-19 Asea Brown Boveri Power switch with arc-quenching chamber and switch-on resistor
DE19809836C1 (en) 1998-03-02 1999-09-09 Siemens Ag High-voltage circuit breaker with a switching rod made of an insulating material
DE102006001241A1 (en) * 2006-01-06 2007-07-12 Siemens Ag Switching point of an electrical switching device and method for moving a switching piece of a switching point
DE102018205910A1 (en) * 2018-04-18 2019-10-24 Siemens Aktiengesellschaft High-voltage circuit breaker with Einschaltwiderstandsanordnung and coupling device
CN109599293B (en) * 2018-12-20 2020-10-23 河南平高电气股份有限公司 Intermittent transmission device and operating mechanism for switching device
CN111261448B (en) * 2020-01-07 2022-07-05 平高集团有限公司 Circuit breaker

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR949494A (en) * 1947-07-11 1949-08-31 Forges Ateliers Const Electr Unbalanced kinematic control systems
US3763340A (en) * 1971-02-12 1973-10-02 Siemens Ag High-voltage circuit breaker equipped with means for placing a resistor in parallel with the breaker contact during breaker closing operations
US4009458A (en) * 1975-04-15 1977-02-22 Hitachi, Ltd. Puffer type gas circuit breaker
DE2949753A1 (en) * 1979-12-07 1981-06-11 Siemens AG, 1000 Berlin und 8000 München HIGH VOLTAGE CIRCUIT BREAKERS
DE3102654A1 (en) * 1981-01-23 1982-08-05 Ernst Prof. Dr.techn.habil. 1000 Berlin Slamecka High-voltage switch with a switchable parallel resistor
CH654139A5 (en) * 1981-04-22 1986-01-31 Sprecher & Schuh Ag HIGH VOLTAGE SWITCH.

Also Published As

Publication number Publication date
DE3664077D1 (en) 1989-07-27
BR8601333A (en) 1986-12-02
US4670632A (en) 1987-06-02
EP0197339A1 (en) 1986-10-15

Similar Documents

Publication Publication Date Title
EP0696040A1 (en) Gas blast circuit-breaker
WO2006097420A1 (en) Electrical contact arrangement having a first and a second contact piece
EP1310970B1 (en) Hybrid circuit breaker with drive
DE2751844A1 (en) DEVICE FOR EFFECTIVE CONTROL ON THE MOVING CONTACT OF A LOAD SWITCH OF THE VACUUM TYPE OF FORCES EXECUTED
EP0197339B1 (en) High tension circuit breaker with closing resistor
DE69708966T2 (en) High Voltage puffer
EP0779637A2 (en) Circuit breaker with closing resistor
DE102014102875B4 (en) Actuating device for actuating a vacuum interrupter, switching device with such an actuator and on-load tap changer with such a switching device
EP0157922A1 (en) High-voltage switch
EP0951038B1 (en) Arcing contact arrangement
EP0024252A1 (en) High-voltage circuit breaker with a resistor and an auxiliary switch
DE3514184A1 (en) High-voltage switch with a switching-on resistor
DE3906786C2 (en)
CH594279A5 (en) Toggle drive unit for medium voltage switch - has symmetrical double spring which reduces bearing load and gives compact construction
DE729599C (en) Switch with arc extinguishing by means of the pressure generated by an auxiliary arc
EP0398461A2 (en) Circuit breaker with an actuating and a locking device for a moving contact
DE2935915A1 (en) ELECTRIC VACUUM SWITCH
DE10048659A1 (en) Switch contact arrangement of a low-voltage circuit breaker with contact force springs
EP3743933A1 (en) Switch element for step switch, and step switch
DE69516790T2 (en) Medium voltage switch or circuit breaker
DE19814398C1 (en) Electrical switching device, in particular electromagnetic switching device with vacuum interrupter
DE3338244C2 (en)
DE4430579A1 (en) All weather gas-encapsulated HV switch
DE2511804A1 (en) Circuit-breaker trip unit - has eccentric compression springs rotating actuating disc through lost motion connection
DE3114837C2 (en)

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH DE FR LI SE

17P Request for examination filed

Effective date: 19870129

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: BBC BROWN BOVERI AG

17Q First examination report despatched

Effective date: 19880928

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE FR LI SE

REF Corresponds to:

Ref document number: 3664077

Country of ref document: DE

Date of ref document: 19890727

ET Fr: translation filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19900215

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19900220

Year of fee payment: 5

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19900523

Year of fee payment: 5

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19900614

Year of fee payment: 5

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19910311

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19910331

Ref country code: CH

Effective date: 19910331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19911129

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19920101

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

EUG Se: european patent has lapsed

Ref document number: 86103192.0

Effective date: 19911009